Multiple-blade junked metal shear

ABSTRACT

A multiple-blade junked metal shear is disclosed including a base, receptacle means, or specially constructed anvil; a hammer or cutter mount with forward and rear portions pivotally connected to the base by pantograph-type arms, the cutter mount carrying cutting blades that cooperate with fixedly positioned blades or knives on the base as the hammer descends; and a forwardly cantilevered platform at forward end which mounts means cooperative with hammer associated means whereby the hammer or cutter mount may descend in a cutting stroke to be returned thereafter to an upper or triggered position preparatory to a successive shearing or cutting stroke; the aforesaid hammer or cutter mount rear portion being adjustable in elevation with relation to the rear pantograph arms so that the cutter or shear blades cut with a scissors effect from front to rear with the base carried blades.

[ Feb. 15, 1972 [54] MULTIPLE-BLADE JUNKED METAL SHEAR [72] lnventor: Wesley D. Ballard, 1311 West Broadway,

Phoenix, Ariz. 85041 [22] Filed: Aug. 19, 1969 [21] Appl. No.: 851,254

Related US. Application Data [63] Continuation-impart of Ser. No. 780,625, Dec. 3, 1968, abandoned, which is a continuation-in-part of Ser. No. 555,187, June 3, 1966, Pat. No. 3,413,914, and a continuation-in-part of 840,902, July 11, 1969.

3,036,516 5/1962 Purcell ..l00/265 X 3,039,343 6/1962 Richards... ..83/923 X 3,237,554 3/1966 Davis ..100/2l8 3,367,019 2/1968 Williamson ..100/98 UX Primary Examiner-Billy J. Wilhite Alt0meyWilliam E. Ford [57] ABSTRACT A multiple-blade junked metal shear is disclosed including a base, receptacle means, or specially constructed anvil; a hammer or cutter mount with forward and rear portions pivotally connected to the base by pantograph-type arms, the cutter mount carrying cutting blades that cooperate with fixedly positioned blades or knives on the base as the hammer descends; and a forwardly cantilevered platform at forward end which mounts means cooperative with hammer associated means whereby the hammer or cutter mount may descend in a cutting stroke to be returned thereafter to an upper or triggered position preparatory to a successive shearing or cutting stroke; the aforesaid hammer or cutter mount rear portion [56] References cued being adjustable in elevation with relation to the rear panto- UNITED STATES PATENTS graph arms so that the cutter or shear blades cut with a scissors effect from front to rear with the base carried blades. 2,986,992 6/1961 Patros et al. ..100/218 2,997,942 8/1961 Dunharn et a1 ..100/265 X 15 Claims, 27 Drawing Figures 2 3 :51; it j t l :e a w l ,LJAAAMMMH. banks 2668 523; T5,: zitfj"-'"'-""-" ;'-'ra isle-Pele "I (ill 160:- In. J6 i lll' rwllllilllllA 'qu '12 250 lgja/ .1 l r. i I! ll o 1 lsot 2% 241 247 PATENTEDFEB 15 m2 SHEET 1 OF 7 WESLEY D. BALLAED INVENTOR 5M ATTORNEY PATENTEBFEB 15 I972 SHEET 2 [1F 7 [V V/ J1 WESLEY D. BALLARD ATTORNEY PATENTEDFEB 1% m2 SHEET 3 BF 7 v A I INVENTOR ESLET D. BALLAED mm: n:

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WESLEY D. BALLAED ATTOk/VE Y MULTIPLE-BLADE JUNKED METAL SHEAR The part of this application added as new relates to a multi ple-blade junked metal shear achieved by providing a hammer specially adapted to mount a multiplicity of cutting or shear blades, with base carrying fixedly positioned, respectively cooperative blades, while the hammer lift and stroke releasing means is provided on a forwardly cantilevered platform as disclosed in the preceding applications; objects of the invention applicable exclusively to the part of this application presenting newly added subject matter are stated as follows:

It is a primary object of the invention to provide a junked metal compressing smasher type machine employable as a multiple-blade junked metal shear by adapting hammer to mount cutter or shear blades and by adapting base to mount fixed, cooperative shear blades and to receive junked metal to be sheared to fall therein and adjacent thereto.

It is another and important object of the invention to provide a multiple-blade junked metal shear or shearing machine of the class immediately hereinabove described, with base providing conveyor means for load delivery thereto, and also providing conveyor means to deliver sheared metal from therewithin, and from adjacent thereto.

It is yet a further object of the invention to provide a multiple-blade junked metal shear or shearing machine of the class immediately hereinabove described, with base providing conveyor means for load delivery thereto, and also providing conveyor means to deliver sheared metal from therewithin, and from adjacent thereto.

It is yet a further object of the invention to provide a multiple-blade junked metal shear of the instant class with rear of hammer adjustably connectable to rear pantograph-type arms for disposition above base at elevation to permit shearing with scissorslike cutting effect from front to rear.

Objects common to hammer descent and lift applicable to all forms of the invention, may be restated, as follows:

It is also another and further object of this invention to provide machines of the class described immediately hereinabove, which include cooperative means in association with hammer lift and cable, that automatically return the hammer to detachably latched, raised position, after each hammer descent.

It is still another object of the inventions to provide machines of this class which provide lost-motion members in the brake lever setting rods disposed between hammer, upon return to upper position, and brake lever aforesaid, thus to provide against part breakage upon hammer overtravel.

Also, it is another important object of the inventions to provide machines of this class which are automatically returned to upper, brake applied, declutched position, by limit switch and solenoid operation.

It is still a further important object of the inventions to provide machines of this class which are automatically returned to upper, brake applied, declutched and safety latched operation by cable actuation of mechanical means to effect clutch engagement.

Furthermore, it is an important object of the invention to provide machines of this class which interpose manual operation to release brake and raise safety latch to initiate each hammer descent.

The objects of the invention applicable only to the disclosure of the parent application, are repeated herewith.

It is consequently a primary object of this invention to provide a junked metal compressing smasher of this class which is adapted to compress metallic objects, as metallic chassis and frame parts, into more compact or reduced size for more economic hauling.

It is also another object of this invention to provide a machine of this class which is preferably portable so that it may be taken to the location of junked metal at remote locations form larger types of metal compacting and processing machinery.

It is a further object of this invention to provide a smasher of this class which includes a heavy hammer that is hinged at one end and adapted to be power lifted and gravity lowered to smash an object, as a junked automobile on a bed or base from which the hammer is pivoted, the base providing sidewalls and a rear end to upstand from the bed to form a die or restraining form, thus limiting the spread of the crushed metal.

It is also an important object of this invention to provide a smasher of this class with bed sidewalls providing openings therein and means to ensure the easy disposition of the lifts of forklift trucks with relation to the bed or base in handling uncrushed bodies onto, and compressed bodies from off, the base.

It is also another and important object of the invention to provide a smasher of this class with a bed adapted to hold a plurality of smashed car bodies, as crushed one at a time, up to the number of crushed bodies that is within the load carrying capacity of the particular forklift truck that is available for feeding bodies to the smasher.

It is still another object of the invention to provide a smasher of this class which may be handled from a truck and tandem wheels onto the ground into smashing position, and back onto a truck and tandem wheels for transportation, in manner that only a pair of jacks is necessary in handling.

It is yet a further object of the invention to provide a metal body crushing machine or smasher of this type which is constructed in manner to require limited head room in transportation so that it may pass under underpasses, overhead bridges, and the like without difficulty.

It is also a further object of the invention to provide a smasher of this type which has a heavily weighted hammer designed to be raised rapidly to be freed to descend by gravity with inappreciable friction and great smashing impact.

Also as a primary object the inventions provide machines which present substantially horizontally disposed crushing contact surfaces upon descent in metal smashing contact, the hammer remaining in constant connection with the hammer lift means.

Other and further objects will be apparent when the specification herein is considered in connection with the drawings, in which:

FIG. 1 is a side elevational view of a smasher comprising an embodiment of the invention with front end pivotally connected to the fifth wheel on the end of a trailer, or behind a truck or prime mover, the rear end being supported on a tandem wheel unit;

FIG. 2 is an isometric view ofa smasher as shown in FIG. I, the machine being shown in operating position ready to crush a second automobile body on top of a first body that has already been crushed as restrained to predetermined spread by the bed of the machine; the position shown also being the position of hammer disposition when the jacks are applied to reload the smasher on trailer and tandem;

FIG. 3 is a small scale side elevational view, showing the machine disclosed in FIGS. 1 and 2 with hammer in the second position for reloading;

FIG. 4 is a small scale side elevational view of the machine shown in FIG. 3, with hammer in the third position of reload- 8;

FIG. 5 is a small scale side elevational view of the machine shown in FIG. 3 with hammer in the fourth or last position of reloading;

FIG. 6 is a plan view of the smasher shown in FIGS. 1, 2 and FIG. 7 is a fragmentary, isometric view of the smasher shown in FIGS. 1, 2, 3 and 6;

FIG. 8 is a fragmentary, transverse elevational view, part in section, looking rearwardly at the station of the hammer pivot shaft, as taken along line 8-8 of FIG. 6.

FIG. 9 is a side elevational view of another embodiment of the invention;

FIG. 10 is a fragmentary plan view, part in section, taken along line 10-10 ofFIG. 9;

FIG. 11 is a fragmentary isometric view of a front end portion of a hammer, as shown in side elevation in FIG. 9;

FIG. 12 is a fragmentary side elevational view, part in section, showing hammer parts in descent, or nearing high impact;

FIG. 13 is a fragmentary plan view, partially diagrammatic, as seen looking down upon the forward portion of the machine including the forward portion of the hammer in lowered position;

FIG. 14 is a fragmentary side elevational view, showing disposition of pivot arms, as taken along line 1414 of FIG. 13;

FIG. 15 is a fragmentary side elevational view of the platform with winch having lifted hammer to uppermost position to contact switch that declutches hoist drive and applies brake;

FIG. 16 is a diagrammatical view of a solenoid operation of clutch and brake levers;

FIG. 17 is an isometric view of an embodiment of the invention comprising the part added as new by this application; such isometric view being for the purpose of showing brake and clutch lever positions with relation to prime mover, transmission, reel, drum, and brake band;

FIG. 18 is an elevational view of platform with clutch engaging and disengaging mechanism thereon, shown partially diagrammatically, with clutch lever in clutch disengaged position; winch turning in freewheeling condition, as hammer descends;

FIG. 19 is an elevational view of platform with clutch engaged and hoist or winch just beginning to lift the hammer; clutch lever accordingly having been urged rearwardly;

FIG. 20 is an elevational view of platform with brake applying and releasing mechanism thereon, shown partially diagrammatically, with brake lever having been moved by hammer urged break rod to brake applied position; safety lock being shown locking hammer in upwardly locked position, release pedal for starting a new cycle also being shown;

FIG. 21 is a large scale sectional elevational view showing spring-urged, lost-motion arrangement for brake setting rod contraction to release brake while hammer arm is still upright.

FIG. 22 is a side elevational view of a machine of the type hereinabove described but with hammer designed to carry metal shearing blades to shear metal as that of junked automobile bodies, and with base equipped with fixedly positioned blades to match the hammer blades in shearing, the machine comprising a preferred embodiment of the inventions added as new by this application, and being termed a multiple-blade junked metal;

FIG. 23 is a transverse sectional elevational view taken along line 23-23 of FIG. 22;

FIG. 24 is an enlarged, fragmentary, side elevational view of teeth comprised in the hammer mounted cutting blade shown in FIG. 22 and also shown in FIG. 25 to be hereinbelow described;

FIG. 25 is an isometric view of the base or bed shown in FIGS. 22 and 23, and illustrative of fixedly positioned blade installation, and also illustrative of conveyor arrangement;

FIG. 26 is an enlarged scale, sectional elevational view, partially diagrammatic, taken along line 26-26 of FIG. 17, showing details of winch clutch and brake operation by mechanical means; and

FIG. 27 is a sectional elevational view of brake lever details of operation, as taken along line 27 --27 of FIG. 26.

Referring now in detail to the drawings of the continuing part of the application, in which like reference numerals are applied to like elements in the various views, a junked metal compressing smasher or crushing machine is shown in detail in FIGS. 1-2, and in FIG. 6-8, with the machine comprising essentially a base 11 and a hammer 12, pivotally mounted on a pivot shaft 13 journaled at either end in brackets 14a, 14b connected to the base 11.

At its forward end the base 1 1 includes a forward cantilever construction which includes a strong upright part 16 upstanding from the forward end of the base 11 and an operators platform 17, cantilevered forwardly therefrom to provide a support for the operational mechanism 18 and to rest, in

transit, as on the rear end of a truck bed or trailer 19, and centrally over a fifth wheel construction 20 carried on the rear end 19, so that a pivot bolt 21 may be installed downwardly, centrally through the platform 17 and through the conventional socket or bore provided therefor in the fifth wheel, thus to provide a vertical pivotal connection between the crusher or smasher 10 and the truck bed or trailer 19 of the prime mover which pulls the smasher.

As its rear end the base 11 includes a rearward cantilever construction 22'with a strong upright part 23 upstanding from the rear end of the base 1 1 and a horizontally extending cantilevered part 24 to the rear thereof having a downwardly opening angle box or rectangular extension frame 25. A tandem unit or assembly 27 of two pair of traction wheels has an upper part comprising a rectangular boss 26 which is received or fitted into the angle frame 25 beneath the cantilever part 24 whereby the rear part of the crusher 10 is supported in transit. Additionally, bolts, not shown, may bolt the rear cantilever part of the tandem unit 27.

The central portion of the base 11 or the base proper Ila, is comprised of longitudinal members in the form of sturdy structural shapes, as inwardly facing channels 28 outermost, with I-beams 29 transversely spaced apart centrally therein between, these beams or shapes being connected forwardly to the rear of the forward upright 16 and rearwardly to the rearward upright 23. As best shown in FIG. 8, these structural members are tied together by a lower baseplate 30 to which they are welded. Also they are tied together by, and welded upwardly to, an upper baseplate 31 which extends over the beams, from just to rear of the hammer pivot to the rear cantilever construction 22.

Additionally at the forward end of the base central portion 11a, the beams 28 and 29 are floored by a top plate 31a forwardly of the hammer pivot. Also, on each side, forwardly, smaller, outwardly facing channels 32 are provided to extend rearwardly and to support on each side the respective brackets 14a, 14b in which are journaled the ends of the hammer pivot shaft 13. Between its respective ends the pivot shaft 13 passes through a succession of spaced-apart upright legs or members of the hammer 12, the outer legs 33:: being connected upwardly to the respective outer, longitudinally extending, structural members or inwardly facing channels or hammer runner members 34.

Between the outer legs 33a, spaced-apart central or inner legs 33b are connected upwardly to a transversely extending structural or hammer plate 35 which extends from channel 34 on one side to channel 34 on the other side. Also, the pivot shaft 13 is supported by longitudinally extending, smaller channels 36, which are disposed between the l-beam 29, and between the l-beams 29 and outer structural members or channels 28, and which extend rearwardly from the forward cantilever upright 16, and which are welded to and supported upon, the lower baseplate 30.

The forward and rear ends of the hammer are tied together, between the ends of the channels 34, by structural plates or angles 37, and spaced inwardly of the outer beams or runner channels 34 the hammer 12 includes l-beams 38, with a larger, central l-beam 39 being spaced centrally between the l-beams 38. Also, longitudinally spaced apart cross-connecting members 37a are provided between the beams as transverse elements. It should be noted that the hammer, for weight, may be constructed of other and heavier shapes, to meet performance requirements, and also the base 1 1 can be constructed of various heavy shapes and forms to withstand the pounding imposed upon it in service.

In order to restrain the automobile bodies crushed upon the base 11 substantially to predetermined plan areas and thickness, respective sidewalls or upright side members 40a, 40b are provided to extend along the base 11 on either side thereof, the walls being comprised of respective forward, central and rear sections 41a, 41b, 410, respectively, with each section comprised of upright beams 42, longitudinally extending runners or upper and central connecting members 43a,

43b, and a longitudinally extending beam, channel or lower runner 44 extending between the uprights 42 for the length of the sidewall sections. The inner surfaces of the sidewalls, which form the die or restraining elements channelizing the spread of junked metal when a car body is crushed, comprise forward, central and rear plates 45a, 45b 45c.

Vertically extending slots 46a, 46b are thus provided between the respective wall sections 41a, 41b and 41b, 410 which are slightly greater in width than the width of the forks or fingers of the conventional forklift truck lifts, as will be hereinbelow described, the slots extending from the tops of the walls downwardly to the tops of the respective runners 44.

Also, in connection with the operation of the forklift trucks which handle the positioning upon, and removal of the automobile bodies from, the base plate 31, a pair of pipe or halfpipe sections 47 are welded to the top plate 31 of the base 12, which extend outwardly from the respective slots 46a, 46b over the plate 31, as indicated in FIG. 2, and in dotted lines in FIG. 6.

At the forward end of each sidewall forward section 41a, a triangularly shaped gusset or forward brace 48 is provided, comprised of a triangularly shaped plate 49 and a diagonally extending structural member, as a channel 50, the bases of the gussets 48 being connected to, and supported upon the respective side channels 32. Also, cross-connecting beams, bars, or brace elements 51 are connected forwardly to the respective rear top corners of the cantilever upright 16 and rearwardly to the top of the respective gussets 48 and forward corners os the forward sidewall sections 41a.

The hammer 12 is lifted and lowered by a cable 52, one end of the cable being dead-ended on the reel drum of a winch 53 mounted on the rear portion of the forward cantilever platform 17. From the drum 53 the cable extends under a sheave of a double-sheave pulley 54 mounted at the top of an A- frame 55 which upstands from the central portion of the hammer 12. In detail the A-frame 55 comprises opposed, transverse structural channels 56 which extend diagonally upwardly from their connections to the hammer side runners 34, to an apex in the form of the housing and mount 57 for the pulley 54, such mount 57 being best shown in FIGS. 2 and 6, but being omitted for purposes of clarity in FIG. 1. The A- frame is completed by a forward diagonally extending I-beam 58 from the central longitudinal beam 39 of the hammer to the apex 57, and by a rearward diagonally extending I-beam 59, from the I-beam 39 to the apex 57, the brace member 59 being in turn braced by a diagonally extending member 60, as indicated in FIG. 1.

The cable 52 extends upwardly around the rear part of the first sheave of the pulley 54 and forwardly and downwardly around the forward part of the first sheave of a double-sheave pulley 61 which is mounted in a bracket assembly 86 carried centrally on top of the top transverse member 62 of a frame 63 which upstands centrally above the cantilever platform 17. Thence the cable 52 extends rearwardly and under and around the rear part of the second sheave of the A-frame pulley 54, and over the back forwardly over the second sheave of the forward pulley 61, and downwardly around the forward part of such second sheave, to terminate functionally in a clamp 64 which is mounted upon a cross brace or cross tie 65, spaced under and parallel with the transverse member 62, and thus between the two forward uprights 66 of the frame 63.

The frame 63 additionally includes two spaced-apart, Iongitudinally extending runners 67 between the tops of the forward uprights 66 and the tops of the rear uprights 68 which upstand from the rear part of the platform 17; a transverse member 87 tying together the tops of the rear uprights 66, and the transverse member 62 tying together the forward uprights 68, as aforesaid. Also, the frame 63 may include adequate conventional cross bracing, or diagonally extending members, not shown, in order to provide clarity of disclosure for the parts shown. The cable 52 extends downwardly from the clamp 64, which dead-ends it to the frame 63, and around a reserve drum 69 which is supported by, and has its shaft journaled in, brackets 70 which are mounted on the forward part of the platform 17.

Since The frame 63 functionally dead-ends the forward end of the cable 52, its component structural elements should be of substantial strength, and in effect the frame 63 comprises a truss. To this end, diagonally extending brace members 71 extend downwardly from the top elements at the rear of the frame 63, through slots 72 in the hammer 12, and are affixed to the top surface of the upper plate 31 of the base portion 1 1a, thus to strengthen the base longitudinally.

A gasoline engine 73 is mounted on the platform 17 to drive the winch 53 which pays out and takes up the cable 52, the engine shaft 74 having a pulley 75 mounted thereon a drive, through conventional sprocket chain or belting, a pulley 76 on one end of a jackshaft 77 which is journaled in, and supported by conventional pillow blocks mounted on the platform 17 to the rear of the engine 73. A pinion 78 is mounted on the other end of the jackshaft 77 to mesh with a large gear 79 on the end of the winch shaft 80, the winch shaft 80 being properly journaled in, and supported by, brackets 81 which upstand from the platfonn 17. A conventional transmission guard 86 is provided for the pulleys 75, 76, as shown in FIG. 7, and a corresponding guard, not shown, may be provided for the gear 79 and pinion 78.

The operators position on the platform 17 is determined by the location of the operating levers 82, 83, which are shown mounted on the platform 17, more or less diagrammatically, to indicate that the operators post must be laterally outwardly from the engine shaft 74, the levers being operatively connected by connection means 84, also indicated diagrammatically in FIG. 7, to select direction of winch rotation (to take up or pay out cable) and to clutch-connect the engine shaft 74 to be driven. Thus, the lever 82, through connection means 84, may operate clutch means, as within the frustoconical engine housing part 85, to connect the engine shaft 74 to drive the winch 53, and the lever 85, by its position, disposes the connection means 84 in manner to determine direction of winch drum rotation. The dotted line arrow thus indicates that the winch drum 53 has rotated in counterclockwise direction to raise the hammer 12.

A strong pipe is shown in the drawings extending transversely across the hammer 12 near the forward end thereof, the pipe 90 being affixed to the structural members 34, 38, 39 as by welding. Also, in FIG. 2, two opposed jacks 88a, 88b, indicated diagrammatically as hydraulic jacks, are shown as being provided with transversely extending support arms or bars 89, from the tops or heads of the jacks 88a, 88b, such supports being of diameter to be slid into the socket providing ends of the pipe 90 when the hammer 12 is raised to position the axis of the pipe 90 in coaxial alignment with the support bar axis when the jacks have been manipulated to raise the support bars to a predetermined level.

If the cable 52 is now freed, by manipulation of the levers 82, 83 on the platform 17, whereby the hammer 12 may descent by its own weight, downwardly from the position shown in FIG. 2, the rearward end of the machine 10 may be scraped slightly forwardly along the ground as the forward end of the machine 10 pivots upwardly about the support and pipe axis into the air, as shown in FIG. 3.

In this position the rear end cantilever 22 is too low to receive a tandem unit 27 thereunder as a first step in transferring the machine 10 from ground to wheeled support. Also, in relationships of hammer pivot 13 with pivot pipe 90 on machines, the hammer 12 could be raised high enough to lift the jacks 88a, 88b off the ground sufficiently to let the machine base 11a return to sit flat upon the ground, the same as shown in FIG. 2, thereby making no progress.

However, if, as shown in FIG. 4, a block or log 92 is placed under the base 11a, a predetermined distance to the rear of the transverse plane of the jacks 88a, 88b, and parallel thereto, the hammer 12 might then be raised to such a height to lift the jacks 88a, 88b from the ground a very slight distance, whereby the forward upper corner of the block 92 becomes the fulcrum, and the forward comer of the cantilever upright 16 moves to the ground as the rear end of the machine 10, including the cantilever 22 is carried upwardly into the air.

The raising of the hammer 12 to the position shown in FIG, 4 has taken the load off of the jacks 88a, 88b, as aforesaid, but when the hammer is lowered again, the jacks seat again and the load is transferred from the block 92 to the jacks and as the hammer is further lowered the forward end of the machine 10 moves upwardly about the fulcrum of pipe 90 and support bars 89 therein, and the rear end of the machine 10 moves downwardly. As this takes place the tandem unit 27 is wheeled beneath the rear cantilever section 22 and manipulated, so that the frame 25 descends, the aforesaid described rectangularly cross-sectioned boss or tandem unit upper frame part 26 is received within the frame part 25 on the underside of the cantilever member 24. Thus, as shown in FIG. 5, the rear end of the machine 10 now bear portion of the tandem unit upper part 26, while the hammer 12 has been fully lowered to rest on the rear part of the base 11a the forward end of the machine 10 still being raised amply above the rear part of a trailer or prime mover 19 which is being backed under such forward end.

At this stage the hydraulic fluid pressure lifting the upper parts of the jacks 88a, 88b may be released to let the upper parts of the jacks descend, and consequently the forward end of the machine 10 may be descend as the rear end 19 of the truck is maneuvered to place its fifth wheel 20 in position to have the fifth wheel connection member 21 installed through the platform 17 to connect the prime mover l9 and machine 10, whereby the machine 10, by the use of the hammer 12 in cooperation with the jacks 88a, 88b, has rapidly been transferred from ground support to wheeled support. It should well be appreciated that the adaptability of the machine 10, which has to be quite heavy to function as intended, to be changed from operative ground support to wheeled support for transport to further locations or junked metal bodies, can provide a highly competitive advantage to an operator of such a machine as will be further emphasized in detail hereinbelow.

The invention is designed to solve at least one economic problem that of inexpensively transferring junked automobile bodies from out-of-the-way locations, or smaller lots, as found in smaller sized cities, to large cities where economy permits the provision of means whereby automobiles bodies may be further processed to be handled in reduced bulk, as in compressed bales, or shredded metal bundles, on the route of junked metal to steel mill furnaces.

The provision of sidewalls to complete a bed, permits a plurality of bodies to be handled, one after another being crushed to the height of the bed, to make a load to the capacity of a forklift truck load. Thus, the quickly crushed loads may be handled from the bed of the machine and loaded to the capacity of a truck bed, or truck load capacity, so that several forklift truck loads can be carried in one hauling truck load, to the site of a massive shredder or baling press, or directly to the site of a steel mill furnace.

An embodiment of the invention introduced by the immediately preceding continuation-impart application is shown in F168. 9-16 disclosing a crushing r junked metal smashing machine 100 comprising a base 101 including an anvil or junked metal supporting box bottom 102 of structural shape and plate construction. From the forward end of the box bottom 102 a cantilever construction 103 extends forwardly to provide a platform 104 on which is mounted the hammer lift apparatus 105 from which extends the cable 106 to the hammer 107 shown mounted by forward and rear pivot arms 108, 109 which dispose the hammer 107 with smashing or crushing under surface 110 above the box bottom 102. Any stop wall 111 may extend across the foot of the box bottom 102 to define the rearward spread of the crushed or junked metal, thus to bond the rear face of the bundle or bale resulting from the fall of the hammer 107. As shown in FIGS. 9 and 10, the stop wall 111 is provided as the front wall of a rearwardly cantilevered section 112, for the same purpose as such section shown in the foregoing forms of invention first disclosed in the parent application, and useful in the unloading and reloading of the smasher 10, when hauling to location by a prime mover.

Sidewalls 113, 114 upstand from the sides of the anvil or box bottom 102, each being comprised from forward end, rearwardly, of successive uprights 115a, 115b, 1 15" as angles, above the floor 116 of the box bottom 102, and mounting a runner, as an angle 1 17a; successive uprights 1180, 118b, mounting a runner 117b; and successive uprights 119a, 1l9b mounting a runner 1170, all as best indicated in H6. 9.

The rear pivot arms 109, on either side of the hammer 107, have their lower ends pivotally mounted on pivot pins 120 which extend transversely outwardly from the sides of the box bottom 102. The upper ends of these arms 109, are pivotally connected to pivot pins 121 which extend transversely outwardly from the side of an upper hammer section l07a which is spaced above the lower hammer section 1071; on each side by forward uprights 122a; intermediate uprights 122b, 1221:, 122d, rear uprights 1222, and diagonally extending rear toe members 122 Runners 123 on the opposed sides of the upper hammer section 107a have rack teeth 123a along the upper rear surfaces thereof into which may fit teeth 124a on a rack 125 on each side of the underside of a counterweight 126 which extends across the upper hammer section 107a. Thus, by selectively moving the counterweight 126 forwardly or rearwardly upon the upper hammer section runners 123 the center of the mass of crushing contact of the hammer 107 may be adjusted in accordance with the center of the mass of a junked metal body, as an automobile to be crushed. FOr in stance, such a shift might be made prior to crushing a series of junked automobile bodies of the same make known to have a center of mass at a predetermined location with relation to the box bottom 102, as loaded thereon.

A cross-frame or transverse wall structure at the rear of the cantilevered platform 104, upstands from the forward end portion of the base 101, and six diagonal brace members 127a, 127b, 1270, 127d; l27e and 127f, with rear, lower ends connected to the box bottom 102, have their upper ends connected to the wall structure or rear cross-frame 130 of the forward cantilevered section 103 at a spaced distance above the base 101, as best indicated in FIG. 9.

A cross-shaft 128, journaled in uprights 129, 12%, H6. 13, which upstand within the forward end of the box bottom 102, extends across the forward end of the box bottom 102, and has six pivot arms 108 mounted thereon, the axis of the cross-shaft 128 being at the same distance above base level as the axes of the pivot pins 120 on which the lower ends of the pivot arms 109 are pivotally mounted. Each runner 128 of the upper hammer section 107a provides a lug 131 on the forward end thereof to receive therethrough a cross-shaft 129 on which the upper ends of the six pivot arms 109 are pivotally mounted. Noticeably the distance between pivot axes on the pivot arms 108 is the same as the distance between pivot axes on the pivot arms 109. Also the distance between the upper pivot axes 129, 121 is the same as the distance between the lower pivot axes 128, 120. Thus a pantagraph arrangement on each side of the forward portion of the hammer 107 ensures that it can move with under crushing surface 1 10 substantially in the horizontal during its smashing or crushing action.

Details of hammer construction are shown in FIGS. 10 and 11, the lower section 1071) being indicated as including a shaped rear end or nose 132 to channelize the rearward and downward movement of the upper rear portion of crushed metal contacted in hammer descent. Noticeably the opposite sides of the lower hammer 107b comprise rail guards 133a, 1331? which extend downwardly below the level of the under sideplate or crushing contact surface 110 of the hammer 107, thus to resist the tendency of parts of the crushed metal from working upwardly between hammer and sidewalls 1 13, 114.

Also, in order to channelize or form the uppermost crushed surface of the junked metal along the opposed upper corners of the mass, diagonally extending plates 134a, 1341: may be disposed with lower edges connected along the inner, lower edges of the rail guard plates 133a, 133b, and upper edges of the plates 1340, 134b connected to the crushing plate or hammer under side surface 110. These elements 133a, 134a, and 133b, 134b are indicated as extending for the full lengths of the respective left and right sides of the lower hammer section 107a.

As shown in FIGS. 9 and 10, plates 1350, 135b, 135C and 135d fill in between the inner legs of the respective upright angles 115a and 115b, lb and 115e, 118a and 118b, and 119a and 119b, on each side, to complete the sidewalls 113, 114. Gaps 136, 137 are thus provided between the uprights 115e, 118a and the uprights 118b, 119a, respectively, on each side, so that the lift prongs of forklift trucks may be inserted just above the floor 116 of the box 102 to handle bodies to be crushed, and after crushing. Wells 138 and 139 are formed or depressed in the floor 116 at spaced-apart distance corresponding generally with the automobile wheel spacing apart. Also, upon first impact junked metal parts are crushed down into the wells 138, 139 and thus latch the automobile body in place against any further longitudinal displacement so that the remainder of impact following this initial fixing of the junked automobile, is directed entirely in vertical crushing. Also, since the wells 138, 139 extend all the way across the box bottom, air compressed by impact of hammer may escape sidewardly through these wells 138, 139 also cleanout can be ac complished sidewardly therefrom. Also, the runner 117b on each side has recess 140 therein, FIG. 9, to receive the outer ends of the pivot pins 121 at the end of hammer drop.

Also, the opposed, pivoted arms 109 have holes 142 therein, so that a safety latch bar, inserted through such holes 142. may rest in the recesses 141 and thus serve as a safeguard in keeping the hammer 107 in upwardly latched position, as when an operator may be working in the box bottom 102. Also, noticeably in FIG. 10, bearings 143a, 1431; are provided on each outer side of the plate 135b, for the pivot shaft 120, and just inboard of the pivot arms 108 thereon. Additional features include soil anchors 144 on each comer of the base 101, comprising anchor plates 145 hinged-upwardly on head pins 146 which extend transversely outwardly at spaced distances above the ground and from the side of the base 101. The anchor plates 145 extend rearwardly and downwardly over guide pins 147 which also extend outwardly from the side of the base 101 and to the rear of, and at a lower lever than the head or hinge pins 146. Thus, as service would ordinarily tend to drive or slide the machine 100 rearwardly along the ground 150 upon which rests the base 101, the anchor plates 145 are driven into the ground 150 to stop any further tendency toward rearward displacement.

Referring now in detail to FIGS. 12, 13 and 14, the upper hammer section 107a is shown as comprised of side runners 123 cross-connected forwardly by a heavy crossbar 148, and cross-connected rearwardly thereof by crossmembers 149. Also, as aforesaid, vertical upright members connect the upper and lower hammer sections 107a, 107b, as shown in FIG. 9; uprights 122a and 122b also being indicated in FIG. 13 below the runners 123 and additionally an upright 122a being shown in FIG. 12. The lower hammer section 107b is indicated in FIG. 13 as having a central, longitudinally extending chamber 151 down the middle thereof, as provided between two parallel extending, longitudinal members 152a, 152b, which may preferably consist of conventional channels, oppositely facing with webs outboard.

In FIG. 13 the space between the channels 152a, 15211, is shown uncovered, for purposes of clarity, but in FIG. 12 this space is indicated as being closed over by strength member plate 153, which extends from channel flange to channel flange, and which can be removably installed to permit removal to give access from above to service the cable 106 and other apparatus within the chamber 151. As indicated in FIG. 12, an eyebolt 154 has its shank extended rearwardly through a dead end plate 155 across the chamber 151 and a nut 156 is threaded onto the end of the shank of the eyebolt 154 to bear on the rear face of the dead end plate when the cable 106 is in tension. The rear end ofa coil spring 157 is dead-ended in the eyelet of the eyebolt 154, and the forward end thereof is connected to a swivel 158 having the rear end of the cable 106 dead-ended to the forward end of the said swivel 158.

The cable 106 extends through a stop washer 159 shown thereon in FIG. 12 just forwardly of the swivel 158, and thence the cable 106 extends through a bore 161 therefore through a stop plate which is located across the chamber 151 a short distance to the rear of the front end of the hammer section 107b. From the stop plate 160 the cable 106 passes over the underside portion of a pulley 162 which is mounted on a shaft 162a which extends across the chamber 151 and is journaled in the webs of the opposed channels 152a, 1521: immediately adjacent the forward ends thereof and forwardly of the stop plate 160. From the underside of the pulley 162 the cable 106 extends upwardly and over a pulley 163 mounted on top the wall 130 and from thence to the drum 164 of a reel 165 supported upon the platform 104.

As shown more or less diagrammatically in FIG. 9, a prime mover, as a gasoline engine 166, is mounted forwardly on the platform 104. The engine 166 drives a pulley 167 which through belt drive 168 drives a larger diameter pulley 169 on a jackshafts, not shown, transmission means 170 on the same jackshaft being indicated diagrammatically as drive-connected to brake and clutch means, not shown, but controlled by the brake lever 171 and clutch lever 172 indicated diagrammatically in FIG. 9. A manually operated lever 173 and lock 174 for the purpose of holding the hammer 107 in raised, locked position, and for then releasing the hammer 107 to descent, is also shown diagrammatically in FIG. 9.

Referring now to FIG. 12, the relative position of hammer 107 and associated apparatus indicate that the hammer 107 has reached the end of crushing stroke, and that the spring 157 has undergone its normal contraction to draw the cable 106 into the hammer chamber 151 for a distance found in practice to be best at approximately 4 feet. At this point all of the cable 106 has been wound off the drum 164 and the cable extends from its dead end knot 175 in the drum 164, FIG. 15, to the groove of the pulley 163 with the shaft 176 of the drum 164 being in alignment with the cable as an extension from its point oftangency on the pulley 163. See cable 106 as shown in dotted lines in FIG. 15.

At this point the cable 106 closes an electric limit switch 177, shown diagrammatically on a bracket which is carried by the upright frame or wall member 130. Closing of the limit switch 177 lets current pass to a conventional clutch moving solenoid 181, FIG. 13, which moves the clutch into enclutched engine drive position, to transfer engine drive through conventional transmission 170, as indicated diagrammatically in FIG. 9, to drive the winch drum 164 counterclockwise in FIGS. 9 and 15 to wind the cable 106 back upon the drum 164.

After the innermost or rearmost 4 feet of cable, as aforesaid, has been drawn out of the hammer chamber 151, the stop washer 159 is brought in contact with the rear side of the stop plate 160, as the swivel 158 is drawn forwardly by the cable 106, and the spring 157 is stretched to fullest intended extent. The hammer 107 is now lifted as the drum 164 continues in counterclockwise drive. When the hammer 107 is completely raised, one of the members 108 (as the one which is shown in front of the cross-brace 127s in FIG. 14), which carries a cross-plate 178 thereon, FIG. 12, is brought into contact with a limit switch 179 on the upright 130 thus to close the limit switch 179 so that a solenoid 182 actuates the application of brake band to the engine drive of the winch drum 164. Then the brake may be set by the lever 173 and locked by the lock mechanism to remain with hammer 107 in upper latched position until manually released.

The electrical diagram shown in FIG. 16 may best be followed through to understand the sequence of hammer raising, releasing, descent to smash, and reraising. As the hammer 107 is raised, as hereinabove explained, the cross-plate 178 strikes the button of LS1 limit switch 179 to close a circuit which includes in series the brake solenoid SOL 182 and a manual pushbutton release 183. The LS1 limit switch 179 being a double-pole switch, it also closes a parallel circuit containing R1 relay 184 therein. When R1 relay 184 is energized it closes relay switch R1 (NO) in a circuit with R2 relay 185 and relay switch R3NC. When the latching R2 relay 185 is energized it closes relay switch R2 (NO) (in parallel with relay switch R1 (NO), and consequently opens a relay switch R2 (NC) in a circuit with relay switch R3 (NO), the clutch solenoid SOL181, and R4 186. Thus, under conditions aforesaid, with full cable on winch drum, the brake drum is applied by SOL 182 operation to brake winch drum rotation, the motor drive is declutched for free-wheeling by SOL 181 operation, and the hammer 107, in fully raised position, may be latched as a safeguard by the application of the lever lock 174 carried by the manually operated lever 173, FIG. 9.

When another vehicle body may be in position on the smasher bed and ready to be compressed, the operator may then remove the lever lock 174, and press the bottom release 183 to break the circuit containing the brake solenoid SOL 182 so that the winch drum may wheel free to let the cable 106 roll off the winch drum 164 following the descent of the hammer 107. The spring 157 within the lower hammer section 10712 tends to add momentum to the start of descent, as it becomes free, upon brake release, to contract for the first time since the end of the preceding hammer descent.

When the hammer 107 reaches the end of its descent (has compressed a vehicle body as much as it will compress) so that the cable 106 from the winch drum 164 reaches the dotted line position of FIG. 15, the LS2 limit switch 177 closes circuit to energize the R3 relay 186 to open relay switch R3 (NC), thus breaking circuit through, and deenergizing R2 relay 185. Also, as this R3 relay 186 opens relay switch R3 (NC), as a latching relay it closes relay switch R3(NO), while the R2 relay 185, upon being deenergized, has opened relay switch R2(NO) and closed relay switch R2(NC). Thus the circuit containing relay switch R3(NO), relay switch R2(NC), clutch solenoid SOL 181 and R4 relay 187 is closed to energize R4 relay 187 to close relay switch R4(NO).

The provision of R4 relay 187 and relay switch R4(NO) insures that the clutch solenoid SOL 181 stays energized to keep the engine enclutched to drive the winch drum 164 after the hammer begins to rise. This need is obvious, since as the cable 106 (dotted position, FIG. first begins to lift the hammer 107, it moves away from the LS2 limit switch 177 so that it can open. The circuit including relay switch R4(NO), relay switch R2(NC), clutch solenoid SOL 181 (energized) and R4 relay 187 (energized) thus continues closed until the hammer 107 is lifted all the way to uppermost position when the cross-plate 178 on a pivot arm 108 actuates the LS1 limit switch 179 to return conditions to the point hereinabove where this description of operations started.

A form of the invention is shown in FIGS. 17-21, which may be termed a preferred form of smasher in that it provides semiautomatic mechanical elements for continued operation. A motor driven arrangement 200 is shown at least partially diagrammatically in FIG. 17, with a Diesel or gasoline engine driven motor 166a is indicated as acting through a transmission represented by the reference numerals 1700, 170b applied respectively to a guarded transmission and machine gear box to transmit drive to a hoist drum 164a to pay out cable 106a. A brake lever 171 is shown diagrammatically with lower end rigidly connected to a horizontally extending rod or shaft 188 in journal bars 189a which extend from one of a pair of support runners 190a, 190b mounted upon the journal providing members, not shown, for the winch drum 164a.

A level 191 is rigidly connected to the left end of the rod or shaft 188, FIG. 17, and a connecting rod 191a on the outer, upper end of the lever 191 makes connection with a brake band 192 about the brake drum 193 of the winch drum 164a. Now, if the brake lever 171 is urged forwardly, (see arrow), as

against the friction interposed by a friction quadrant, not shown in FIG. 17, but indicated by the quadrant 194, FIG. 20, then the lever 191 is swung downwardly (counterclockwise) so that the brake band 192 is applied to brake the drum flange or brake drum 193.

Considering FIG. 17 the clutch lever 172 has been urged forwardly, as per dotted line arrow, to pivot counterclockwise the rod or shaft 195 which is rigidly connected thereto, the shaft 195 being journaled in journals provided by journal bars 189b which are indicated as extending forwardly from the support runner 1901). This has lifted a connecting rod 196 shown as extending upwardly from the outer end of a lever 197 for upper end pivotal connection across the bifurcated right end of a bellcrank lever 198 with junction mounted for the bellcrank lever to pivot centrally upon a transverse pin indicated as extending horizontally from a support, as from the top face of the rearward support runner 1901:.

The upper end of the bellcrank lever 198 carries a fork 198a thereon to engage a flange 1990 of a cone-type clutch 199 with cone 199k out of engagement within the drum flange 164b of the winch drum 1640 with the clutch 199 in leftward position as shown in FIG. 17 and also in FIG. 18. Then if the clutch lever 1720 is now moved rearwardly as indicated by the full line arrow in FIG. 17, the cone surface 1 99b of the clutch 199 will be moved to the right and into internal engagement, not shown, within the drum flange 16412, as the clutch 199a, to which the clutch cone 19% is rigidly connected, is moved outwardly upon the drive shaft 176a, and into driving connection therewith, as by cooperative keyway and spline or key means, not shown.

The lower end of the clutch lever 172 has a spring 201 shown as extending forwardly and upwardly therefrom, as will be described hereinbelow. Also a clutch lever setting rod 202 has its bifurcated forward end fitting 202a pivotally connected across the clutch lever 172 at a point above the spring 201 and below the clutch lever pivot shaft or axle 195. The operation of the rod 202 will be hereinbelow described.

Also in FIG. 17 a brake setting device 203 is indicated as providing a forward rod or rod portion 203a to bear against the rear face of the brake lever 188 above the brake lever pivot shaft or axle 188. This device is indicated as including a floor supported lost motion cylinder or housing 2031; and a rearwardly disposed rod or rod portion 2030. The operation of the brake setting device 203 will be explained in further detail hereinbelow in relation to description of FIGS. 20 and 22.

Referring now to FIG. 18, the apparatus 205 for releasing the hammer 107a to descend and crush a junked vehicle, then to be returned automatically to upwardly, releasably latched position, is shown as having released the hammer 1070 for descent, and the hammer is just approaching the bottom of its stroke, or the lowermost crushing or compressing position. In this view most all of the cable 106a has been unreeled from the cable drum 164a and the position is being approached where the cable 1060 will extend, as all unreeled, along a line between the drum shaft 176a (on which the drum 164a has been freewheeling), the cable dead end notch 175a, and the groove of the pulley 163a.

As shown, the cable 106a is still spaced from contact with a contact plate or disk 204 on the forward end of a pawl lift rod 206 which extends horizontally through mounting straps 207 on opposite ends of a vertically disposed mounting plate 208 carried by a frame post or upright a, which upstands above the platform 104a. The rod 206 carries a wedge 209 which extends through a earn slot 211, (FIG. 19), provided by a pawl 210 shown in FIG. 18 as having longitudinally (vertically) spaced apart vertical slots 212 therein, with machine bolts 213 extending through the upper ends of the slots 212 and into the upright 130a, whereby the pawl 210 is mounted on the upright 130a and in relation to the wedge rod 206.

In FIGS. 18 and 19 the pawl 210 is shown as having its lower end 210a tapered to a forwardly provided point to engage with ratchet teeth provided in a ratchet 214 which is disposed to slide longitudinally, or from front to rear, in a guide slide 215 mounted at an appropriate elevation on the upright 130a below the pawl mounting machine bolts 213. The ratchet 214 has upwardly facing teeth 216 therein to be selectively engaged by the pawl tooth 210a in accordance with longitudinal, horizontal movement of the ratchet 214.

Ratchet movement is effected by a bellcrank lever 217 having a slot 218 in its upper leg 2170 for engagement with a cross-pin 219 which extends transversely horizontally from the forward end 220 of the ratchet 214. Such bellcrank lever 217 pivots centrally upon a cross-pin 221 which extends transversely, horizontally from the upright 130a, and the lower leg 217b is pivotally connected to the bifurcated rear end 202b of the clutch lever setting rod 202 as introduced with description of FIG. 17. In FIG. 18 the aforesaid shaft or axle 195 to which the clutch lever 172a is rigidly connected, is indicated as journaled in a quadrant bracket 222 in addition to the journal bars 189b shown in FIG. 17. Also in FIG. 18, the spring 201, introduced in description of FIG. 17, is shown having its forward end connected to a bracket 223 provided by the platform 104, and stretched by the clutch lever 172a in this clutch disengaged position.

Referring now to FIG. 19, the hammer has reached the bottom of its descent and all the cable 106a has been paid out, and the dead center cable position has been reached, with shaft 176a, dead end notch 175a, and groove of pulley 163a in alignment. The cable has thus contacted the foot or disk plate 204 on the forward end of the wedge or pawl rod 206 to move it to the right. As a consequence the wedge 209 has lifted the pawl 210 from successive ratchet tooth contact by lifting the pawl 210 with relation to the machine bolts 213 within its slots 212, the cam slot in the pawl 210 being engaged by the tapered wedge 209 at areas higher in elevation. At this occurs the aforesaid spring 201 may contract and draw the lower end of the clutch lever 172a forwardly as the upper end of the clutch lever 172a is urged rearwardly as indicated by full line arrow in FIG. 19.

As hereinabove described, as the clutch lever 172a has had its upper end urged rearwardly by the contraction of the spring 201, clockwise rotation of the clutch lever cross-shaft 195 draws the right leg of the bellcrank lever 198 downwardly, so that the fork 198a urges the clutch flange 199a to the right. This brings the surface of the clutch cone 199b within the drum flange 164b into engagement with the inner, drive transmitting surface of the drum flange 164b, not shown, as the clutch flange 199a is forced into drive establishing engagement, not shown, with the winch drum shaft 176a, as driven from the gearbox 170b, in turn driven by the transmission 1700 from the motor 166a.

The winch drum 164a is now driven in direction to raise the hammer and wind up the cable 106a on the drum. When most of the cable has thus been would up, the hammer approaches upper or raised position and a forward pivot arm 108a approaches the vertical near the upright 130a. Finally, the pivot arm first strikes the ratchet 214 to urge it to the left so that the pawl 210 descent into ratchet tooth engagement, as in FIG. 18, whereas the pawl lift or wedge carrying rod 206 is also contacted by the aforesaid pivot arm 108a and moved to the left to the relative position indicated in FIG. 18. Obviously, as the cable 106a has been would up it has moved to the left with relation to the contact plate or disk 204 on the left end of the rod 206, and now, when the hammer is drawn back up to upper position, the disk plate 204 is returned to the same proximity to the cable 106 shown in FIG. 18.

Heretofore the description of operation has related generally to the clutch setting operation and the brake lever 171a and its associated elements have been omitted from FIGS. 18 and 19 for purposes of clarity. As shown in FIG. 20, the brake lever 171a has been moved to brake setting position as indicated by the dotted line arrow, also shown in FIG. 17. The aforesaid brake lever cross-shaft 188, introduced in description of FIG. 17 as being journaled in journal bars 189b, is also indicated in FIG. 20 as being joumaled in a brake quadrant bracket 194 supported by the platform 104a, and by the reference it may be established that the support runners 190a, 19% must also be supported substantially at the elevation of the platform 104a. Also, as heretofore introduced in description of FIG. 17, the brake setting device 203 comprises a rod portion 203a forwardly to contact the brake lever 171 above the cross-shaft 188, a cylinder or sleeve assembly 203b supported by an upright stand 224 above the platform 104a, and a rear rod portion 2036 which terminates rearwardly in a bearing plate or disc to be contacted by a pivot arm 108a of the hammer when it is in fully lifted position. A guide clamp or bracket 226 at forward and rear face of the upright or frame member a receives the rear rod portion 203C therethrough and a spring 227 surrounds the rear end portion of the rod portion 2030 to bear forwardly against the upright 130a and rearwardly against the bearing plate or disc 225.

The sleeve assembly 203b, as best shown in detail in FIG, 21 includes a cylindrical body member 228a, which is centrally affixed to the top of the stand 224, not shown. The cylindrical body member 228 has the rear end of the forward rod portion 203a connected into its closed forward end 228b.

The sleeve assembly 203b has the flange 228c on the forward end of the rear rod portion 2030 insertable into the rear end of the cylindrical body 228a to bear on the rear of a biasing spring 228d to urge its forward end against the inner face of the forward sleeve closure 228b. A rear closure cap 2282 is insertable over or around the rear rod portion 203a and threadable upon the cylindrical body member 228a to complete the sleeve assembly 203b There is thus provided a lost motion arrangement, to be hereinbelow described, between brake lever 171a forwardly, and pivot arm 1080 of the hammer 107a.

As the hammer 107a has ascended, the aforesaid pivot arm 108a, which carries a transversely horizontally extending anchor pin 229, approaches a latch member 230 in the form of a bellcrank lever with rearward arm 230a having specially formed teeth 230C comprising the under side thereof. The bellcrank latch member 230 pivots centrally upon a transversely horizontally extending pivot pin 231 on the upright 103a, and a spring 232 having lower end connected to the forward upper corner of the forward bellcrank lever arm 230b, and upper end connected thereabove the upright 130a, thus to bias the rear bellcrank lever arm 230a downwardly.

A connection fitting 233a on the upper endof a flexible cable 233 makes connection to the under side of the forward arm 23% of the bellcrank lever 230 and extends rearwardly and downwardly over an upper pulley 234a mounted on the upright member 130a, and on the rear side of a lower pulley 234b mounted therebelow on the platform 104a. Thence the flexible cable 233 extends to the lower leg 235a of a bellcrank lever 235 with central pivot 2350 just above the level of the platform floor 130a and with the upper leg 235b of the bellcrank lever 235 serving as a foot treadle.

It thus occurs that hammer pivot arm contact, as the hammer 107a is returned to fully raised position, acts upon one means that automatically declutches the winch drum 164a from motor drive, FIGS. 18 and 19; acts upon another means independently to set the brake band 192 tightly against the brake drum 193, FIG. 20; and acts upon a third means independently to latch the hammer 107a in upper position, FIG. 20.

The lost motion assembly 203b serves one purpose of safeguarding against breakage, which otherwise might occur in case of hammer lift overtravel with rigid brake setting rod assembly, the breakage thus tending to occur in the chain of mechanism from and including brake band, and elements therefrom back to the pad or plate 225 which immediately contacts hammer pivot arm. Also, the provision of resilient means in the brake setting rod assembly 230 buffs overtravel of the anchor pin 229, which tends to ride upon the rear face of a tooth 230c forwardly of the notch between teeth, but for the rearward urging of the biasing spring 228d, FIG. 21, which returns the hammer 107a from any overtravel to tooth notch engagement of latch lever 230 with anchor pin 229.

Noticeably in the clutch lever quadrant 222 no teeth are indicated and the clutch lever is controlled by physical attachment to the clutch lever setting rod 202 which starts the chain of elements ending in the clutch cone 1992: being latched in surface disengagement with the inner surface, not shown, of the drum clutch 1641;, this being accomplished at the end of the aforesaid chain by the engagement of the pawl tooth 210a with a ratchet tooth 216. On the other hand, the brake lever quadrant 194, is shown as being provided with a toothed quadrant 194a by the dotted line arc. FIG. 20.

In order to set the hammer 107a back in crushing operation, the operator first puts his foot on the foot treadle 235b provided by the bellcrank lever 235. As the hammer 107a is not latched upwardly by a rigid brake lever setting rod, the bellcrank lever arm 230a can be pivoted upwardly by the downward travel of the flexible cable 233 as the mass of the hammer 1070 does not enter into holding the anchor pin 229 in tooth engagement, as this effect is counterbalanced by virtue of the yieldability of the biasing spring 228d in the brake lever rod sleeve assembly 2031).

With the operators foot pressing down the foot treadle 235b, he now manually urges the brake lever 171a rearwardly toward the dotted line position shown in FIG. 20. Normally, with conventional lever pawl, quadrant tooth engagement, difficulty would be experienced in urging the brake lever 171a rearwardly out of brake quadrant tooth engagement, if opposed by a rigid brake setting rod disposed between the brake lever 171a and hammer 107a. However, with the lost-motion sleeve assembly 2031; interposed in the brake setting rod assembly 203, the operator can disengage the brake lever pawl from the tooth it has been engaged with so that the brake band 192 can release the brake drum 193 enough to let the winch drum 164a start freewheeling. Also, at this point, the momentum of the mass of the hammer 107a, in descent, will be abetted by the contraction of the hammer spring 157, FIG. 12, as at this instant the spring 157 is relieved of the force that has been holding it with washer 159 against the rear face of the stop plate 160.

Referring now to the form of the invention shown in FIGS. 13, and 16, the current, indicated as 110 volt, VAC, may also be supplied by DC voltage. Also, all of the apparatus shown in FIG. 16, including the manually operated master switch 236, and excluding limit switches and solenoids, may be provided in a panel, not indicated in the drawings, but disposed at any preferred location.

Although one form of the invention shows the hammer lift and release apparatus of electrical type, and another form shows hammer lift and release all by mechanical means, the invention is not thus limited, and hydraulic systems, pneumatic systems, and various combinations of electrical, mechanical, hydraulic, and pneumatic systems may be employed.

The embodiment of the inventions disclosed herein as new and applicable to a multiple blade junked metal shear or shearing machine, shown in FIGS. 22-25, may be described herein as follows:

A multiple-blade junked metal shear 240 comprises a base 241 with a hammer or cutter mount 245 pivotally mounted on forward pivot arms 248 and rearward pivot arms 249, with the lower ends of the forward pivot arms 248 pivotally mounted on a lower, forward cross-shaft 247 extending across the base, and the lower ends of the rearward pivot arms 249 pivotally mounted on a lower, rearward cross-shaft 247 extending across the base. Also, the upper ends of the forward pivot arms 248 are pivotally mounted on an upper, forward crossshaft 244 extending across the forward end of the hammer 245, the upper ends of the rearward pivot arms 249 being pivotally mounted with relation to the hammer 245 by means to be hereinbelow described.

The cross-shafts 246,247 have their ends journaled in respective parallel extending, spaced-apart structural members as channel beams 242 mounted upon a base plate 243 which extends for substantially the length of the machine. The

hammer or cutter mount 245 is of cross section shown in FIG. 23 with upper portion 245a of width to achieve weight, and with the lower portion 245k of reduced dimension to pass between the inner face of upright members 2510, 251k comprising the sides of a pressure pad or sheared metal receptacle or box 250. Inner plates 252a, 2521) upstand from a floor plate 255 and determine the receiving space shape of the box 250 in transverse cross section. Noticeably the cross-sectional dimension is greatest across the lower part of the box space, the inner plates 252a, 2521) tapering upwardly to minimum dimension to receive the punch or shearing lower portion 245b of the hammer 245 between the upper portions of the plates 252a, 252b, with slightest shearing clearance therebetween.

Above the plates 252a, 2521; respective shear blade mounting bars 2530, 253b extend in parallel, spaced-apart relation or the cutting or shearing length of the box 250, the upper, inner portions of the bars 253a, 253!) being relieved to receive therein the respective fixed shearing blades 254a, 254)) in manner that the respective inner faces of the blades 254a, 2541: are spaced apart a distance to receive the hammer portion or punch 245b therebetween with slightest shearing clearance.

The box inner plates 252a, 252b and the shear blade mounting bars 253a and 2531; are held in place and reenforced by a series of transversely extending gussets 256 with right and left gussets being relieved on inner edge to receive the respective blade mounting bars 253a, 2513b and the respective inner plates 252a, 2521:. Also the right and left gussets 256 are notched or relieved along lower outer edge to receive respective foot channels or runners 2560, 256b therein. When these gussets 256 have been welded inwardly to the outer surfaces of the respective inner plates 252a, 252b, and to the outer and lower surfaces of the respective blade mounting bars 253a, 153b; and outwardly to the flanges of the foot channels 2650, 256b; and along their under edges to the floor plate 255, a box 250 of substantial strength results to withstand spreading, warping or buckling under the continuing repeated impact of the shearing hammer 245 upon workloads of metal.

As best shown in FIG. 23, the receptacle or pressure pad box 250 has its floor plate 255 supported upon the spacedapart channel beams or support runners 242, and the space under the area of hammer impact may be reenforced between the channels 242, and between the floor plate 255 and baseplate 243 by concrete 257. As best seen in FIG. 23, the box or pressure pad receptacle 250 substantially exactly straddles the channel beams 242, with the hammer center of impact falling substantially centrally between the upright members 251a, 251b, for obtaining best results in shearing operatrons.

Machines 240 of the instant type are adapted to shear metal at such a rate that the junked metal may be brought thereto by conveyor means, and also, the sheared metal may be conveyed by conveyor means out of the box 250, and away from the side of the box opposite the side of metal entry. As shown in FIGS. 23 and 25, a belt conveyor 258 can deliver junked metal, as in the form of junked automobile bodies, to the top of the box 250 on the right side thereof as one looks forwardly. The conveyor belt 2580, not shown in width, should be approximately 6 feet in width or a convenient width to accommodate an automobile body of above average maximum transverse dimension. The roller 259 over which the conveyor belt 258a passes at its delivery end is indicated as supported or journaled at each end of the journal brackets, a journal bracket 261 being shown in FIG. 23 indicating that it may be supported at the opposed ends of the box 250 from end gussets 256.

A guide plate 261, shown in FIG. 23, is shown disposed over the tops or upper edges of the right gussets 256. Thus nothing can call on the entry side of the box 250, but metal brought to the box for shearing is assured substantially total service, as will be hereinbelow described. For instance, with a junked automobile body 15 feet long arriving on the conveyor 258, the forward l8 inches of length is disposed to the left of the box opening, the next 18 inches of length is disposed over the box opening, and the remainder of the automobile body falls to the right of the opening or on the delivery or junked metal approach side of the box 250.

In the first stroke of the hammer 245, the forward 18 inch of length thus fails, and is urged, to the left by the hammer tapered side 260a. A removable side cover plate 262 is installed on the left side gussets 256 with the top portion 262a to cover the tops thereof and with the tapered or apron portion 26217 to cover the gussets against any metal falling into the spaces between gussets 256. Thus the first 18 inches of the vehicle length falls off to the left, and, (as indicated in FIG. 22, and as best shown in FIG. 23) onto a belt conveyor 263. At the same time the second 18 inches of junked metal length is sheared from the leading 18 inches length, and from the trailing part of the junked metal vehicle therebeliind, and the sheared part beneath the hammer is forced down into the interior of the box 250 below the hammer contact 245b and between the inner plates 252a, 25217. Also, the tapered right side portion 26Gb of the hammer 245 flattens the portion of the junked metal vehicle immediately to the rear of the second 18 inches of length, and urges it back to the right, and thus further back onto the conveyor belt 2580.

As best indicated in FIG. 23, the belt conveyor 263 may be mounted in manner to use the left foot channel 256b to 265the journals for the right ends of the shafts of the conveyor rollers, as the roller 264 over which the conveyor belt 263a turns. Outwardly the roller 264 has journal support by a channel 256C provided with the belt conveyor 263, to extend parallel with the foot channel 256b, with the outer end of the roller shaft 2640 being indicated in FIGS. 22 and 23 as mounting a pulley 264b that is driven from a driven belt from a pinion 265a on the end of the shaft 265 b of the drive motor 265, supported above the floor plate 255 by a suitable mounting base 266.

The conveyor belt 263a discharges at the rear end of the machine 240 over a roller corresponding with the roller 264 and having the end of its shaft 264c journaled in the rear end portion of the channel beam or runner 256a. Such channel beam or runner 256c is supported by longitudinally spacedapart, transversely extending I-beams 267a, 267b, 267e, shown in FIG. 22, with the forward l-beam 267a also being shown in FIG. 23. The upper flange is removed from the right portion of these l-beams so that they may extend under, and add support beneath, the part of the floor plate 255 that overextends the left beam channel 242, and so that they may be connected to, or abut with, the aforesaid left beam channel 242.

The belt conveyor 268 which transfers the second 18 inch length of sheared and compressed metal from the box 250 is indicated in FIG. 23 as having an intermediate roller 269 with an axle, pipe or shaft 269a passed therethrough with ends to pass through bushings 252e, 252d in the respective inner plates 252a, 252b where these plates upstand above the floor plate 255 with the greatest distance between inner plates. The axle 269a is indicated as being restrained from transverse movement by having its end threaded and having conventional nuts 26917 threaded upon the axles ends.

At the box forward end, as shown in FIG. 25, a roller, corresponding with the roller 269, has its shaft or axle ends 269d journaled in lugs 252e, 252f that extend forwardly from the respective inner plates 2520, 252b. A drive motor 270 is shown in FIG. 25 as mounted on the floor plate 255 with motor shaft 270a mounting a pinion or pinion pulley 270b, which, through a drive belt 270e, drives a pulley 2692 on the aforesaid axle end 269d of the forward or drive roller for the conveyor belt 2680.

The rear end portions of the inner plates 252a 252b may have lugs extending rearwardly therefore corresponding with the lugs 252e, 252f, shown in FIG. 25. Preferably such lugs may extend rearwardly to substantially the extent that the runner beam 256c and the foot channel 256b may extend rearwardly, whereby the discharge of the sheared and compressed junked metal from the box conveyor 268 may occur in transverse alignment with the discharge from the side conveyor 263, as shown in FIG. 22.

Noticeably in FIGS. 22 and 23, a motor 265 is mounted forward of the belt conveyor 263 to drive the conveyor belt 263a thereof, the pinion pulley 265a on the motor shaft driving the pulley 264b to turn the forward roller shaft 264a to which the roller 264 is connected. As shown in FIG. 23, the roller shaft 2640 may be connected by a coupling 274 to the shaft (269e, FIG. 25) of the rear roller, corresponding with the roller 269 of the belt conveyor 268. Thus, in this manner, the single motor 265 can drive both conveyors 263 and 268. Also, in FIG. 25, by dotted line extension 269f it is indicated that the roller 2690 may be connected to the roller shaft 264a, whereby, from the position shown the motor 270 may also drive the drive roller 264 for the conveyor belt 263a of the belt conveyor 263. Note that in FIG. 25 the channel or runner 256a shown in FIGS. 22 and 23, is omitted for the sake of clarity.

In relation to the operation of shearing, it is pointed out that, as a special feature, the shear blades, or fixedly positioned inserts 254a, 254b, should be of tempered steel to stand up to the usage imposed. Also, the hammer contact block 245b that cooperates with the shear blades or inserts 254a, 254b, should carry shearing means of tempered steel. Such inserts are best constructed as saw tooth arrangements of assemblies 271a, 271b, to obtain a scissors effect in shearing, also best to hold the junked metal, as an automobile body, from displacement as such metal is sheared and compressed.

As shown in FIG. 24, each of the shearing assemblies 271a, 271b, carries a plurality of teeth 272 in the form of rectangular blocks, which are installed in succession in the assembly recesses 273 provided along the lower left and right sides of the hammer contact portion 24512. By relieving a block of material from the lower right and left rear portion of the hammer contact or shearing member 245b, a relieved space 275 is provided on each side of the hammer. Then, the 45 relieved spaces 276 are further provided to extend upwardly from the space 275 and the block-shaped teeth 272 are then installed to provide the jagged, downwardly extending lines of teeth 272 on each side of the hammer contact or shearing portion 245b. Each tooth 272 is shown installed by two flat head machine screws 277 with the shanks of the machine screws 277 being threaded into the holes 278 drilled transversely into the hammer portion 245b. Also relief holes 281 are provided above the upper corners of the 45 spaces 276, so that teeth having worncorners may fit in place and square when the worn corner of a tooth is reversed upon being reinstalled.

With the teeth 272 on each side all installed, each assembly, as the assembly 271b, FIG. 22, discloses a sawtooth or zigzag edged knife or cutter blade with a space 279 for each tooth, the junked metal along the shear strip is first crimped into the spaces 279 and then an 18 inch strip is sheared out, with there being approximately 2 inches of crimped metal. If it were not for the spaces 273 permitting the first contacted metal to be crimped thereinto, the downward travel of the heavy hammer 245 from front to rear would tend to urge the metal load or workpiece rearwardly. However in the instant case the first crimped metal retards rearward sliding, and the workload can move no further rearwardly than the most rearward teeth can extend at their lowest position.

Noticeable features of construction reside in the fact that a crosstie member or channel 282 extends transversely across the rear face of the rearmost gussets 256 to serve as a strength member to keep the uprights 251a, 251b from spreading in service. Also, for the same service, at the front of the box or receptacle 250, with upper flange below the lowest point of hammer travel at this particular station, a crosstie member or channel 283 is provided across the forward face of the most forward gussets 256. The box 250 is braced against rearward displacement or sag under hammer impact by diagonally extending cross braces 284, FIG. 22, with upper, rearward ends connected to the upper faces of the most forward gussets 256, as shown in dotted rectangles in FIG. 25, and with lower forward ends connected to the forward portion of the floor plate 255. As indicated in FIG. 25 the bracket 261 on the foremost right gusset 256, also shown in FIG. 23, supports and provides journal for the roller shaft 259a of the roller 259 of the load feed conveyor 258, a corresponding supporting bracket, not shown, being provided on the rearmost right gusset 256.

The operation of the hammer 245 with relation to its delivery of shearing stroke impact to the workload as disposed over the pressure pad or box receptacle 250, with its fixed shear blades 254a, 254b, can be adjusted from that of a pantograph, or actuated parallelogram. Thus, by selective adjustment, the distance between the upper pivot points of the arms, 248, 249 may be increased by increments, whereby the hammer teeth contact with the workload is rear to front, the hammer sloping slightly downwardly toward the rear. Also, by selective adjustment, the distance between the upper pivot points of the arms 248, 249 may be decreased by increments, whereby the hammer teeth contact with the workload is from front to rear. This may be accomplished by providing insert blocks 280 for insertion in transversely aligned recesses 285 on the opposite sides of the upper hammer portion 2451:, FIG. 23.

As best shown in FIG. 22, each of the opposed insert blocks 280 is disclosed as having five horizontally aligned holes therein being 286a, 286b, 2860, 286a. As indicated in this view, the opposed pins 287 extending through the upper ends of the transversely aligned pivot arms 249 have been inserted into the second holes 286k to connect the machine base 241 to the hammer 245 for pivotal, modified pantograph-type movement with relation thereto. In this relationship the under surface of the hammer contact 245b together with the teeth 272 on each side, will descend with the hammer under surface at a slight slant to the horizontal, highest point rearwardly, so that upon the shearing stroke, the teeth 272 begin contacting the workload from front to rear.

Obviously, with the pins 287 in opposed holes 286e, the upper distance between pins 244, 287 is greater than the base distance between the pins 246, 247, the hammer tilts rearwardly and downwardly, so that the rearmost teeth 272 engage the workload first, with engagement of the teeth being by scissors action successively forwardly thereafter. It follows that with the pins 287 in opposed central holes 286c, a strict parallelogram, or pantograph action is obtained, with the cutting edges of the teeth 272 all descending in the same horizontal plane. The choice of hammer contact tilt for scissors action, front to rear, or rear to front, may thus be selected to best serve the character and condition of the workload of junked metal, as to its density, components, disposition, distribution, and the like.

Also, the distribution of the center of impact of the hammer 245 may be shifted longitudinally and also sidewardly, as indicated partially diagrammatically in FIG. 22. This is accomplished by providing a counterweight 288 of high specific gravity, as of lead, to seat upon the top of the hammer upper portion 245a. The counterweight 288 has teeth 289 formed in the under side thereof to mesh with teeth 290 of a rack of transverse teeth cast in the upper surface of the upper hammer portion 2450. The heavy counterweight 288 may be lifted by conventional handling apparatus for disposition selectively longitudinally along the rack of teeth 290 to shift the center of hammer impact longitudinally. Also, as the rack teeth 290 extend all of the way across the top of the hammer while the counterweight 288 is of lesser transverse width in special cases the counterweight may be shifted laterally and disposed with centerline off the longitudinal center line of the hammer.

Cable connection to the hammer in the form of invention shown in FIGS. 2725 is the same as in the hammer shown in the electrically actuated embodiment of FIGS. 9-16, and also shown in the mechanically actuated embodiment in the mechanically actuated embodiment of FIGS. 944, and FIGS. 17-21. As shown in FIGS. 22 and 23, a pipe 291 is shown cast in the hammer 245, to extend longitudinally for the length thereof and in the upper part of the lower hammer portion 245b. An anchor plate a is affixed in the rear portion of the pipe 291, and the shank end of an eyebolt 1540 is passed through a central bore through the plate or disk 155a and a nut or pair of locked nuts 156a serves as stop means upon the shank 154a, all correspondingly as shown in the embodiment of the cable anchorage disclosed in FIG. 12.

And also correspondingly, the spring 157a that has its rear end connected to the eyelet of the eyebolt 154a, FIG. 23, has its forward and connected to the rear member or eyelet of a swivel 158a, FIG. 22. The cable 106a extends forwardly from the forward end of the swivel 158a and through a stop washer 159a and thence through a bore or hole 161a in a forward stop plate a near the forward end of the pipe 291, as such is cast in the hammer 245. Further, correspondingly as shown in FIG. 12, a pulley 162b is provided in the forward end of the pipe 291 with axle or shaft 162a extending transversely thereacross, the pulley 162b being thus disposed so that the cable 106!) may pass thereunder and upwardly around the pulley 162b to extend upwardly and forwardly thereof.

In order to ensure against the machine 240 being displaced under the strenuous impact of repeated hammer blows, anchor plates 145b may be placed upon the base 241 to be lodged in the ground 150b on the opposite sides of the forward end thereof. Each anchor plate is mounted by a pivot head 146b which extends transversely from a bore in the side of a base channel 242. Then the anchor plate extends with the inside of its curved surface over a guide pin 147b, which also extends transversely from the respective base channel 242 whereby the anchor plate or blade 1451) is directed at a suitable angle of penetration into the earth 15Gb. Also, anchor plates in correspondence with those on the forward end of the base 241 may be suitably located in connection with the rear end of the base 241.

correspondingly as shown in FIGS. 13 and 14, a plurality of transversely spaced-apart pivot arms 248, corresponding with the arms 108, are mounted with lower ends pivotal upon the cross-shaft 246 and with upper ends pivotal upon the crossshaft 244 which extends through transversely spaced-apart lugs 131a that extend forwardly from the forward end of the hammer upper portion 245a. Each pivot arm 248 is slidably in contact with a diagonally extending platform brace 292 with upper end connected upwardly and forwardly to the wall or upright member 130a at the rear of the platform 104a, and with lower end connected rearwardly to the base or floor plate 243. As indicated in FIG. 14, the pivot arms 248 extend in sliding or adjacently supported relationship with the platform braces 292.

The platform shown in FIG. 24 may be considered the platform shown in FIGS. 18, 19 and 20, with the apparatus shown in FIG. 21 mounted thereon. Thus the cable 106a extends over a pulley 163a mounted on top of the rear wall, frame, or upright 130a and around the drum of a winch 164a. The winch 164a is indicated as driven by a gasoline engine 166a which, through a pinion pulley 167a on the engine shaft, drives a pulley 1680 included as part of a transmission 170a which drives through further transmission means the shaft 1760 of the aforesaid winch drum 164a. A conventional brake lever 171a is shown diagrammatically in FIG. 22 to brake the rotation of the winch drum 164a, andto release the brake on the cutting stroke of the hammer. Also a conventional clutch lever 172a is shown diagrammatically in FIG. 22 to release the clutch from driving engagement with the winch drum 164a to permit it to wheel free on cutting stroke, and to engage the winch drum 164a for engine drive on the lift stroke.

Without the contact rod 203e, indicated in dotted lines in FIG. 22, and the mechanical apparatus associated therewith in FIGS. 17-20, inclusive, the machine 240 will not operate automatically mechanically to return the hammer 245 to upper position after each cutting stroke of the hammer. Also, without the limit switchs 177,179 indicated in dotted lines in FIG. 22, and the electrical apparatus indicated as being associated with the limit switches in FIGS. 15-16, the machine 240 will not operate automatically electrically to return the hammer 245 to upper position after each cutting stroke of the hammer. However, in all cases, the providing of the spring 157a as the cable end portion that dead-ends the rearward end of the cable 106a in the hammer 245, ensures that all slack is taken up during the freewheeling of the winch drum as the hammer falls through cutting contact.

Thus, without automatically mechanical, or automatically electrical hammer lift apparatus, a machine 240 is still most serviceable with cable 106a dead-ended rearwardly, as hereinabove described. For instance, with winch drum declutched, the operator manually releases a lever lock 174a indicated diagrammatically as being adapted to hold the hammer 245 in upwardly latched position, as latched about a pivot arm 248, the manually operated lever 173a bearing the lever lock 174a then being pivoted about its platform floor mounted pivot 173b to inactive position. At the same time the operator has moved the brake lever 171a to release the brake drum 164a for freewheeling. The hammer 245 thus descends into junked metal cutting or shearing contact. If the junked metal, after shearing impact, still stands comparatively high, the freewheeling winch drum still tends to unreel all the cable 106a thereon. But the spring 157a, in any event, can contract to take up all of the slack in the cable, at whatever elevation the hammer may have reached at the end of shearing stroke.

Then the operator, seeing the hammer 245 at the end of shearing stoke, urges the clutch lever 172a to enclutch the winch drum 164a for engine drive, and the winch drum beings to reel up the cable 106a. When the stop washer 159a abuts the stop plate 160a, the pull on the cable 106a then begins to lift the hammer 245 as the pivot arms 248, 249 are pivoted counterclockwise, as viewed in FIG. 22. Then, when the operator observes the hammer 245 has neared approximate upright position, he operates the clutch lever 172a to declutch the winch drum 164a from engine drive. Also, as security, he can manually urge the lever 172a to the right, FIG. 22, so that the lever lock 174a, shown at least in part diagrammatically, may be manually releasably latched about a pivot arm 248, or a part thereof.

When the junked metal shear 240 shown in FIGS. 22-25 is equipped with the limit switches 177, 179, indicated in dotted lines in FIG. 22, and with the apparatus disclosed in FIGS. 12, 13, and 16, the automatically, electrically actuated shearing and lift strokes are in accordance with the smasher operation hereinabove described, pages 2528, inclusive. In this case the rod 2030 and associated apparatus are not operated.

When the junked metal shear 240 shown in FIGS. 22-25 is equipped with the rod 2030 and apparatus shown associated therewith in FIGS. 17-21, and with the switches 177,179 shown in dotted lines in FIG. 22 not operated, the automatically, mechanically actuated, shearing and lift strokes are in accordance with the smasher operation hereinabove described, pages 2937, inclusive.

The apparatus shown at least partially diagrammatically in FIG. 17, as typical of conventional engine driven winch operation, is shown to larger scale, and for a more graphic picturization, in FIG. 26. Thus, by way of reiteration in relation to larger scale disclosure, it can be stated: The engine 166a, through the transmission 170a and gearbox 170b, establishes driving connection with the shaft 19% which extends free through the winch drum 164a on which the payout cable 106a is dead-ended. The winch drum 164a has a left end flange 295 with a reduced diameter bearing flange 295a outwardly thereof and journaled in the gearbox 170b. At its right end the winch drum 164a has a right or brake flange 193 and outwardly thereof a reduced diameter right end clutch cylinder 16412 which extends through a bearing ring 296a of a supporting pillow block 296.

The clutch cylinder 164b is hollow toward its outer end and provides frustoconical internal clutch surface 1640 for engagement by a frustocone 1990 provided on the clutch shaft 19%. The right end portion of the clutch shaft 19% provides a clutch ring 199a thereon, and the end thereof is slidably journaled in a supported pillow block or bearing member 297.

As hereinabove described movement of the clutch lever 172a in directionindicated by the arrow or toward the viewer rotates upwardly the lever 197 which is fixed rigidly to the clutch lever shaft 195 to which the clutch lever 172a is also rigidly fixed. The ends of the clutch lever shaft 195 are jour naled in bearing or journal brackets 18917 as indicated. The lever 197 has a rod 196 with lower end loosely connected about a yoke pin across the outer bifurcated end thereof while the upper end of the rod 196 is loosely connected about the yoke pin (at to the yoke pin aforesaid) of the bifurcated outer end 1980 of a bellcrank lever 198. The bellcrank lever 198 is pivotally mounted upon a pivot pin 198b that extends transversely (or horizontally) outwardly from housing or frame, as do the aforesaid journal brackets 18% for the clutch lever shaft 195. The inner, upper leg 1980 of the bellcrank lever 198 provides the clutch fork that operates against the opposite sides of the clutch ring 199a to shift the clutch shaft 19% longitudinally. Thus, if the clutch lever 172a is moved in direction aforesaid, the bellcrank lever fork 198a moves to the left to move the clutch cone 1996 out of engagement with the clutch surface 1640, and the winch drum 164a is set freewheeling so that the cable 106a unreels as indicated.

The yoke 202a (about the yoke pin of which the lower end of the clutch lever 172a is pivotally connected) is shown in proper relationship in FIG. 26, but, for purposes of demonstration, the spring 201 which constantly urges forwardly on the lower end of the clutch lever, (FIG. 18), is shown in FIG. 26 at 90 to its proper relationship. Obviously then, considering FIG. 18, it can be seen that when the clutch lever 172a is urged in direction to declutch the winch drum 164a from engine drive, then it has to be latched in such position or else the spring 201 will urge the clutch lever 172a to pivot in clockwise relationship, FIG. 18, and clutch engage the winch drum 164a for engine drive.

As hereinabove set forth, the brake lever 171a is rigidly connected to the brake lever shaft 188, which is journaled in bearing or journal brackets 189a. If the brake lever 171a is urged toward the viewer, as indicated by the arrow in FIG. 26, such movement will pivot the lever 191 downwardly so that the connecting rod 191a, with upper end rigidly connected to the brake band 192, and with lower end, loosely pivotally connected about the yoke pin, not shown, across the bifurcated outer end of the lever 191, moves downwardly with relation to the brake drum 193, more firmly to apply the brake band 192 and brake the winch drum 164a against being rotated, as by unscheduled enclutching the winch drum 164a for engine drive.

When the operator is ready to release the brake and unlatch the hammer for descent, he may have strength in his hand to draw the pawl lift lever 298a (pivoted at 298b) against the brake lever handle 298, whereby the pawl lift rod 298e, pivotally connected across the pawl lift lever 298a at 298b, may lift the pawl 300 upwardly and out of engagement with that quadrant tooth 194a with which it has been engaged when the brake has been set. In this upward movement of the pawl lift rod 2980 it has been held by the guide band 299 in its substantially parallel, slightly spaced relationship from the brake lever 171a.

With the pawl 300 lifted out of tooth engagement, the operator still would not be able to move the brake lever 171a opposite the direction indicated in FIG. 26, or in clockwise direction, FIG. 20, if a rigid rod or assembly of members extended between the particular hammer pivot arm in longitudinal alignment therewith. However, when the operator urges the pawl released, brake lever 171a rearwardly against the rod 203, this urges the spring 228d, FIG. 21, against the flange 2280 on the forward end of the rod 2030, (within the lost motion assembly housing 203b) so that the pad 225 bears more heavily against the opposed hammer pivot arm 248 (dotted lines, FIG. 22) to kick off the hammer for downward descent, and to permit the brake lever 171a to be moved further in direction of brake release. The operation of the foot peddle 235 to release the latch 230 is identical with the hammer 245,

(FIGS. 22-25) as with the smasher hammers hereinabove described.

The machines 240 are of transverse width to receive the junked metal, as of an automobile body, at the rate of say 3 feet of longitudinal length per stroke of the hammer, a leading 18 inch strip falling onto the side conveyor and the second 18 inch strip falls into the box or receptacle. In this manner, after the fifth stroke, the average vehicle would be consumed in process.

Referring now to FIG. 23, although it may be asserted that this transverse cross-sectional view has been taken generally along line 23-23 of FIG, 22 license for departure has been taken in that the left part thereof has been taken at substantially the station of the forward roller of the side conveyor, whereas the part of the section showing the conveyor inside the box is stated to have been taken at the station of an intermediate roller. Also, as regard to FIG. 24, this view may be reconciled with the showing of the tooth assembly shown in FIG. 22 by stating that one tooth block has been left out of the fragmentary elevational view of FIG. 24 in order to show the machine screw holes into the relieved side of the hammer contact portion.

The invention includes many variations, modifications, and embodiments that may fall within the spirit thereof, and the claims submitted are illustrative of included exemplary combinations of structures.

I claim:

1. (Amended) A multiple-blade junked metal shear comprising a base with a forward cantilevered platform, said base including upstanding side members, with a junked metal receiving box provided therebetween, a hammer mounting transversely spaced-apart toothed blades to move in shearing adjacency with opposed, fixedly positioned blades on said base for shearing junked metal and forcing it into restrained disposition between said side members and under said hammer and sidewardly of the side member opposite the side member in direction of metal entry, pivot means transversely across the forward portion of said base adjacent said platform, pivot arms interconnecting said pivot means and said hammer, hammer lift means on said platform, cable means continuously connected to said hammer during descent and return to upper position, and cooperative means operable in association with said cable means and said hammer lift means to return said hammer to lifted position after each descent into processing contact with junked metal disposed on said base, pulley means being provided in said hammer and on said platform and said cable means extending under said pulley means in the hammer and over pulley means on the platform and having one end dead-ended on said hammer lift means and the other end dead-ended on said hammer.

2. A multiple-blade junked metal shear as claimed in claim I in which the end of said cable means dead-ended to said hammer comprises a spring.

3. A multiple-blade junked metal shear as claimed in claim I in which said hammer lift means comprises a reel drum on which said cable is wound, and engine means for driving the reel drum, said engine drive being declutched as said hammer is lifted, and said shear additionally including a releasable brake to hold said hammer in upwardly latched position.

4. A multiple-blade junked metal shear as claimed in claim 1 in which said hammer includes a selectively movable counterweight to locate center of smashing impact.

5. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes limit switch means.

6. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes lost motion, yieldable means.

7. A multiple-blade junked metal shear as claimed in claim I in which said cooperative means includes latch means actuated upon ascent of said hammer to lifted position to engage said hammer in upwardly, releasably latched position, and

manually o erable to release said hammer for descent.

8. A mu tiple-blade unked metal shear as claimed in claim I in which said cooperative means includes a winch drum with brake band applied by brake lever operation to brake said winch drum in cable wound up, hammer uplifted position, said winch drum being set freewheeling by manual operation of brake lever to pay out cable for hammer descent.

9. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes toothed latch mechanism manually operable to release said hammer for descent.

10. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a conveyor between said side members.

11. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a conveyor adjacent and parallel to one of said side members to carry away sheared material falling to one side of said one side member and not between said side members.

12. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a conveyor between said side members and a conveyor adjacent and parallel to one of said side members to carry away sheared material falling to one side of said one side member and not between said side members.

13. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a feed conveyor adjacent to and perpendicular to one of said side members to feed scrap between said side members.

14. A multiple-blade junked metal shear, as claimed in claim 1, in which said pivot means may be selectively positioned with relation to said hammer, whereby said hammer may be disposed to cut with successive tooth contact from rear to front.

15. A multiple-blade junked metal shear, as claimed in claim 1, in which said pivot means may be selectively positioned with relation to said hammer, whereby said hammer may be disposed to cut with successive tooth contact from front to rear. 

1. (Amended) A multiple-blade junked metal shear comprising a base with a forward cantilevered platform, said base including upstanding side members, with a junked metal receiving box provided therebetween, a hammer mounting transversely spacedapart toothed blades to move in shearing adjacency with opposed, fixedly positioned blades on said base for shearing junked metal and forcing it into restrained disposition between said side members and under said hammer and sidewardly of the side member opposite the side member in direction of metal entry, pivot means transversely across the forward portion of said base adjacent said platform, pivot arms interconnecting said pivot means and said hammer, hammer lift means on said platform, cable means continuously connected to said hammer during descent and return to upper position, and cooperative means operable in asSociation with said cable means and said hammer lift means to return said hammer to lifted position after each descent into processing contact with junked metal disposed on said base, pulley means being provided in said hammer and on said platform and said cable means extending under said pulley means in the hammer and over pulley means on the platform and having one end dead-ended on said hammer lift means and the other end dead-ended on said hammer.
 2. A multiple-blade junked metal shear as claimed in claim 1 in which the end of said cable means dead-ended to said hammer comprises a spring.
 3. A multiple-blade junked metal shear as claimed in claim 1 in which said hammer lift means comprises a reel drum on which said cable is wound, and engine means for driving the reel drum, said engine drive being declutched as said hammer is lifted, and said shear additionally including a releasable brake to hold said hammer in upwardly latched position.
 4. A multiple-blade junked metal shear as claimed in claim 1 in which said hammer includes a selectively movable counterweight to locate center of smashing impact.
 5. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes limit switch means.
 6. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes lost motion, yieldable means.
 7. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes latch means actuated upon ascent of said hammer to lifted position to engage said hammer in upwardly, releasably latched position, and manually operable to release said hammer for descent.
 8. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes a winch drum with brake band applied by brake lever operation to brake said winch drum in cable wound up, hammer uplifted position, said winch drum being set freewheeling by manual operation of brake lever to pay out cable for hammer descent.
 9. A multiple-blade junked metal shear as claimed in claim 1 in which said cooperative means includes toothed latch mechanism manually operable to release said hammer for descent.
 10. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a conveyor between said side members.
 11. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a conveyor adjacent and parallel to one of said side members to carry away sheared material falling to one side of said one side member and not between said side members.
 12. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a conveyor between said side members and a conveyor adjacent and parallel to one of said side members to carry away sheared material falling to one side of said one side member and not between said side members.
 13. A multiple-blade junked metal shear, as claimed in claim 1, which additionally includes a feed conveyor adjacent to and perpendicular to one of said side members to feed scrap between said side members.
 14. A multiple-blade junked metal shear, as claimed in claim 1, in which said pivot means may be selectively positioned with relation to said hammer, whereby said hammer may be disposed to cut with successive tooth contact from rear to front.
 15. A multiple-blade junked metal shear, as claimed in claim 1, in which said pivot means may be selectively positioned with relation to said hammer, whereby said hammer may be disposed to cut with successive tooth contact from front to rear. 